High speed punch



Oct. 3, 1961 c. s. JACKOWSKI 3,002,678

ma SPEED PUNCH Filed July 22, 1960 4 Sheets-Sheet 1 FIG. 1

IN VE N TOR CHARLES S. JACKOWSKI A T TORNE) C. S. JACKOWSKI HIGH SPEED PUNCH Oct. 3, 1961 4 Sheets-Sheet 2 Filed July 22, 1960 Oct. 3, 1961 c. s. JACKOWSKI HIGH SPEED PUNCH 4 Sheets-Sheet 3 Filed July 22, 1960 FIG. 3

91 FIG.4

DISPLACEMENT 1961 c. s. JACKOWSKI 3,002,578

HIGH SPEED PUNCH Filed July 22, 1960 4 s s 4 SIX SLOTGENEVA 44's" 104.8" 224.8 284.8 44.8 l04.8

WHEEL 25 MOVE I I MOVE I I MOVE I I MOVE DWELL H DWELL DWELL H CAM 18 L L o 1 o PULSE MAGNET 62 3 ELEMENT I6 o o ,I 0 INTERPOSER PUNCH 1s o 210 sec so 180 ROTATION 0F CAM 18 (DEGREES) FIG.6'

United States Patent 3,002,678 HIGH SPEED PUNCH Charles S. .lackowski, Endicott, N.Y., assignor to International Business Machines (Iorporation, New York, N.Y., a corporation of New York Filed July 22, 1960, Ser. No. 44,729 14 Claims. (Q1. 234-414.)

This invention relates to machines for applying a code marking to a record, such as tape or a record card, and more particularly to punching machines wherein the record is advanced stepwise past a punching station and the record is punched while stationary between stepwise movements.

It has recently been proposed to provide a punching machine comprising a single rotary cam having a cam surface, preferably defined by a plurality of lobes of identical and symmetrical configuration, for controlling operation of an associated reciprocable punch through the medium of a selecting lever, an interposer and a punch restoring lever that are engageable with said cam surface. Although this punching machine operates very satisfactorily, the interposer constantly rides on the cam surface of the rotary cam during idling cycles (i.e., during cycles when the punch is not being operated). This tends to heat and wear the interposer and thus reduce its useful life and hence undesirably limit the rate capability of the machine.

The principal object of this invention is to provide an improved record-marking machine of the above general type embodying rotary cam means for controlling an associated punch or other marking member through the medium of a plurality of cam-controlled elements which effectively engage the cam means only when the particular associated marking member is to be actuated. According to the invention, the improved marking machine com prises holding means, such as an electrically controlled armature, normally holding one element in a position in which it is effectively disengaged from a rotating cam and in which it abuts an interposer to operatively hold another element eifectively disengaged from the cam, said other element being pivotally connected to the interposer. When the holding means is rendered ineifeotive, such as by electro-magnetic attraction of the armature, the one element is resiliently biased into contact with the cam and thus out of abutting contact with the interposer, thereby permitting the other element to be resiliently biased into contact with the cam which preferably, though not necessarily is the same cam. As the cam rotates, said other element will interpose the interposer between the one element and a marking member, and then the cam will act through said one element and interposer to move the marking member to a marking position.

The improved marking machine also preferably comprises a rockable restoring lever having one arm connected to the marking member. When the member is moved to marking position, the restoring lever is rocked one way through the medium of said one arm to move its other arm toward a cam which preferably, though not necessarily, is the same cam which is engaged by the one and other elements. After the member is marked, the cam acting through said other arm will positively rock the restoring lever the opposite way to restore the member to noimal position.

The foregoing and other objects, features and advan- "ice 2 tages of the invention will be apparent from the following more particular description of a preferred embodiment of the invention, as illustrated in the accompanying drawings, wherein:

FIG. 1 is a schematic elevation view of a punching machine embodying the invention shown associated with a portion of a record card transport system;

FIG. 2 is an enlarged view of a portion of FIG. 1 showing one of the punches and its corresponding control mechanism positioned as during an idling cycle;

FIGS. 3 and 4 are views like FIG. 2 except with the punch and its control mechanism shown in respective positions assumed after inception of a punching cycle before the punch starts to move down and after it has moved almost to its lowest point;

FIG. 5 is a section view taken along the line 55 of FIG. 4; and

FIG. 6 is a diagrammatic timing diagram showing the relative times at which various components are actuated.

Description As shown in FIG. 1, the improved machine illustrated therein comprises briefly means, designated generally 11, for moving successive record cards 12 stepwise along a card feed path, from right to left as viewed in this figure, relative to a single bank of vertically reciprocable marking members, such as punches 13, only one of which is shown. This bank preferably comprises a number of punches 13 equal to the number of columns (rather than rows) provided on the record card 12 (for example, punches for a conventional 80-column 12-row card), so that the cards will be punched in paralle (that is, row by row). Operation of each punch 13 is independently controlled by a corresponding punch control mechanism including an element or lever 14, interposer 15, interposer-like element 16, restoring lever 17 and rotary cam 18, each of identical configuration, and a preferably electrically controlled holding means 19.

In the embodiment illustrated, the means 11 comprises two transversely spaced intermittent drive mechanisms, only one of which is shown in FIG. 1. Each. drive mechanism comprises a pair of drivers 25 constantly rotated counterclockwise such as by a drive pulley 21 through the medium of a belt 22. Each pulley 21 is keyed to, and driven counterclockwise by, a common drive shaft 23 that extends transversely of the machine below the punches 13 and is journaled in side frames (not shown). Each driver 20 is rotatably mounted on a suitably supported transverse pin or shaft 24 and carries two diametrically opposite drive pins 25 equally offset from the aXis of said pin. As each driver 24 rotates counterclockwise, its pins 25 will alternately enter successive adjacent radial slots in a corresponding Geneva wheel 26 and rotate such wheel clockwise through equal small angular increments. Each wheel 26 and a corresponding pressure roll 27 are keyed to a respective shaft 28 suitably journaled in a respective side frame above the card feed path, each roll 27 being the driving roll of a respective set of intermittent feed rolls 27, 2.9 through which cards are adapted to be fed stepwise by and as the particular roll 27 is rotated intermittently by its Geneva wheel 26. The respective sets of rolls 27, 29 of each drive mechanism are spaced along the card feed path at opposite sides of the bank of punches 13 and at a distance less than the distance between the leading and trailing edges of a card 12 so that the card will be picked up by the leftmost set of rolls 27, 29 before passing out of the rightmost set, thereby to assure uninterrupted control over stepwise movement of the card past the punches 13.

Each idler roll 29 is rotatably carried on a respective pin 31} that, in turn, is carried by the mid portion of one arm 31 of a corresponding bell crank 32. A suitably anchored spring 33 hooked to the other arm 34 of each bell crank 32 pulls on the latter to rockably bias it about a fulcrum pin 35 to maintain a corresponding roller follower 36 in contact with a respective cam 37, each such follower being carried at the outer end of its respective arm 31.

Each cam 37 is keyed to, and constantly rotated counterclockwise by, a suitably driven drive shaft 38 journaled in the side frame. Keyed to each shaft 38 so as to be constantly rotated thereby is a driving roll 39 of a corresponding set of rolls 39, 40. The rolls 40 are idler rolls rotatably mounted on pins 41 carried by the side frames. One set of rolls 39, 40 is disposed ahead of the punches 13 and between the adjacent set of intermittent feed rolls 27, 29 and the brushes 42 of a sensing station 43, said sets of rolls being less than one card length apart. The other set of rolls '39, 41 is positioned downpath of the punches between the adjacent set of rolls 27, 29 and the brushes 44 of a sensing station 45, said sets of rolls also being less than one card length apart. This spacing between the various sets of rolls 27, 29 and 39, 40 assures that cards will always be fed into the rolls of one set before being released by the preceding set.

In view of the spacing just described, the following arrangement is provided to prevent a card from being subjected concurrently to the constant driving movement of the rolls 39, 40 and to the intermittent stepwise movement of the adjacent rolls 27, 29. When either follower 36 rides onto the high portion of its constantly rotating cam 37, the corresponding roll 29 will be rocked downward by bell crank 32 against the action of spring 33 to spread the rolls 27, 29, as shown in FIG. 1, to render said rolls ineffective to impart a stepwise driving motion to the card. On the other hand, each constantly rotating roll 39 has a recess 46 in its periphery so that the rolls 39, 40 will be ineffective to frictionally drive a card except whenthe card is pinched between roll 40 and the non-recessed part of roll 39. The manner in which these rolls 27, 29 and 39, 40 are rendered selectively effective will be described in the summary of operation.

The punch control mechanism is best shown in FIGS. 2 through and will now be described. As illustrated, the cams 18 are mounted side-by-side and keyed to, and constantly rotated clockwise by, a drive shaft 47 journaled in the side frames; however, if preferred, a single cam roll may be used instead of 80 transversely spaced cams. Each cam 18 has a cam surface defined by two lobes of identical and symmetrical configuration, such that their respective low points L, L (see FIGS. 2 through 4) are diametrically opposite each other and arranged at 90 to their respective diametrically opposite high points H, H.

Each lever 14 is roekably fulcrumed on a pin 50 carried by a respective lug of a fixed support 51. A spring 52 is anchored to support 51 and connected to one arm of lever 14. Spring 52 biases lever 14 clockwise about pin 50 to bias a follower 53, which is carried at the outer end of the other arm of said lever, into contact with cam 18. Each interposer 15 is pivotally connected by a pin 54 to said other arm of the corresponding lever 14 at a point intermediate pin 50 and follower 53. Each interposer 15 is laterally confined with slight clearance between a guide pin 55 and the top of the corresponding punch 13 to assure that the interposer will be constrained to move generally transversely of the punch axis as lever 14 rocks on pin 50.

Each element 16 is rockably supported on a fixed fulcrum pin 56 and biased clockwise about said pin by a suitably anchored spring 57 to bias a follower 58 at one end of said element into contact with the corresponding earn 18. However, the holding means 19 normally latches element 16 in a normal position, in which it is shown in FIGS. 1 and 2. In this position, follower 58 is held efiectively disengaged from cam 18 and said follower abuts the free end of the interposer 15 'for applying thereto a force which acts through pin 54 and lever 14 to also hold follower 53 disengaged from the cam.

Each holding means 19 preferably comprises an armature 59 that normally is biased toward element 16 by a spring 66 so that it can interlockingly engage a shoulder 61 provided at the end of said element remote from follower 58. When a corresponding magnet 52 is energized, it will attract the associated armature 59 and thus free the element 16 so that it will be rocked by spring 57 and carry follower 58 into contact with cam 18.

Each restoring lever 17 is preferably in the form of a bell crank rockably supported at its knee on pin 56. A hook-like end 63 of one arm of lever 17 projects into a notch in the side of the corresponding punch 13 to provide an interlocking type connection between said element and punch. A light spring 64 biases the lever 17 clockwise about pin 56 to normally, through hook 63, hold the punch 13 in a normal or retracted position in which it is shown in FIG. 2 and which is defined by contact of a shoulder on the punch with a stop plate 65. A follower 66 formed at the end of the other arm of lever 17 is also normally held efiectively disengaged from cam 18 by the action of spring 64. It is to be noted that the cam 18 acts through lever 17 to positively move the punch 13 to retracted position and that the spring 64 is merely strong enough to maintain the .punch in retract ed position against vibration and gravity.

Energization of each magnet 62 may be controlled selectively in any desired manner. In the embodiment illustrated, the various magnets 62 may be energized either by the brushes 42 of sensing station 43 or the brushes 44 of sensing station 45. Station 43 is used if information sensed from one card 12 is to be sent to a calculator (not shown) to compute results to be punched in that card or the preceding card; whereas station 45 is used if information sensed from a preceding card is to be punched in a subsequent card. a

Each of these brushes 42 or 44, as the case may be, complete a corresponding electrical circuit when they detect perforations in a card 12 as it moves between the brushes and respective contact rolls 70, 71; it is to be noted, however, that each such circuit is opened by a circuit breaker cam in the manner well known to those familiar with this art during the card point cycles that the brushes wipe the spaces between successive cards 12, in order to prevent undesired energization of the punch control magnets 62 at such time.

As a card 12 is fed leftward by feed rolls (not shown) past the sensing station 43 and into the adjacent rolls 39, 40, the non-recessed part of said roll 39 will effectively engage and starts to frictionally drive the card further past the sensing station. When the leading edge of the card reaches the new side of the punches 13, the recessed part of the roll 39 will come into registry with the card, and the rolls 39, 40 will cease driving the card. The card will then be registered in proper position relative to the punches 13 by a card registering mechanism 75.

This mechanism 75, as illustrated, comprises two sets ofcooperably connected levers 76, 77 each set being disposed just inside the transversely spaced side frames (not shown) and only one set of which levers are shown in FIG. 1. Each lever 76 is generally T-shaped and rockably fulcrumed substantially at the junction of its three arms on a transverse rod 78' carried by the side frames. A suitably anchored spring 79 is hooked to one of the arms of each lever '76 to bias it counterclockwise about rod 78 and thereby maintain a respective roller follower 80, carried by another of said arms, in contact with a corresponding rotary cam 81. Each cam 81 is keyed to, and constantly rotated by, the drive shaft 38 nearest station 43.

Each card registering lever 77 is rockably supported on a pin 82 carried by the third arm of the corresponding lever 76. A light spring 83 is hooked to the spring-carrying arm of each lever 76 and to one end of each lever 77 to bias such lever 77 counterclockwise about its pin 82 to raise above the card feed path a hook 84 formed at the other end of lever 77. However, each hook 84 will be depressed aginst the light bias of its spring 83 by the oncoming edge and then the under side of an advancing card 12. Each cam 81 is of such configuration that each hook 84, after popping up behind the trailing edge of a card 12 and through a longitudinal slot in a bed plate (not shown), will be moved leftward and register the card. This leftward movement of hooks 84 is effected when followers 80 ride onto the low parts of cams 81 and springs 79 rock levers 76 counterclockwise for swinging the pins 82 and hence the levers 77 leftward. After the card 12 has been moved leftward to its initial or registered position in which it is shown, followers 80 will ride onto the high parts of their cams 81 and cause the levers 77 and hooks 84 to move rightward preparatory to registering a succeeding card 12.

. Meanwhile, as the card 12 is successively advanced stepwise past the punches 13 and then withdrawn by the leftmost set of rolls 39, 40 past station 45, the suc ceeding card 12 will be moved onto the bed plate and advanced between the rightmost set of feed rolls 39, 40. This succeeding card 12 will be advanced leftward by the rightmost rolls 39, 40 until the recessed part of roll 39 registers with such card, as heretofore explained. The hooks 84 will register such succeeding card 12 before it is gripped and advanced by feed rolls 27, 29. It is to be understood that through suitable gearing (not shown) rotation of the drivers 20, earns 18, 37, 81 and constantly rotating feed rolls 39 is synchronized such that the drivers and cams 18 make a complete revolution every two marking or so-called card point cycles, whereas the feed rolls 39 and earns 37, 81 will make a complete revolution every complete machine cycle. Assuming that a conventional twelve-row record card 12 is used and being punched in paralle as above defined, each machine cycle will equal 16 card point cycles, twelve of which correspond to the times necessary to index a conventional twelve-row card and the remainder corresponding to the entry and exit times for a card.

Summary of operation Assume that the magnets 62 of the various holding means 19 are deenergized; and that the cams 18, 37, 81, drivers 20, and driving feed rolls 39 are rotating in synchronism, in the manner above described. Assume further that a particular card at the punch station has been driven leftward by the rightmost feed rolls 3-9, 40 until the recess 46 of roll 39 registered with the card to cause rolls 39, 40 to cease driving the card, and that the card has thereafter been registered by the mechanism 75 in the position in which it is shown inFIG. 1. Under the assumed conditions, all parts will be in the relative positions in which they are shown in FIGS. 1 and 2.

Follower 36 will new ride onto the low part of cam 37 to permit spring 33 to bias the corresponding bell crank 32 counterclockwise about pin 35 and thereby through pin 30 elevate the corresponding roll 29 to pinch the card between rolls 27, 29. Thereafter as drive pins 25 successively enter the slots in the Geneva wheel 26, the particularcard 12 will be indexed leftward stepwise relative to the punches 13, first by the rightmost Geneva wheels 26 and sets of rolls 27, 29, then for one or two card point cycles by all wheels 26 and rolls 27, 29 and then solely by the leftmost wheels 26 and sets ofrolls 27, 29. Meanwhile, the card registering mechanism 75 will be controlled in the manner already explained.

Assume now, for sake of illustration, that the brushes 44 of sensing station 45 are being used to read the cards 12 for so-called gang punching operation, in which information on a preceding card is punched into the card at the punch station. Under this condition. each of the eightly brushes 44 (one for each column) are connected to corresponding ones of the magnets 62 via circuitry above explained. As long as the magnets 62 remain deenergized, their armatures 59 will maintain the respective elements 16 latched, as best shown in FIG. 2. With elements 16 latched, their followers 58 will be held elfectively disengaged from the earns 18 and through abutting contact with the corresponding interposers 15 also hold the associated follower 53 effectively disengaged from the cams. The restoring levers 17 and punches 13 will also remain stationary because the followers 58 will not effectively engage the rotating earns 18.

In subsequent description the timing relationships during a punching or marking cycle will be expressed in terms of the degrees that the low points L of the cams 18 are rotated relative to a reference point Z. It will also be understood that the punches may be operated at rates exceeding 22,000 card point cycles per minute without changing the configuration of any of the parts; however, as the punching rate increases, the pulse must be given to a particular magnet 62 correspondingly earlier because a constant pick-up time interval is required after a pulse signal is received and before sufficient flux is built up to attract the armature 59. The magnet pulse times hereafter stated will correspond to operation at the rate of 10,000 card point cycles per minute with a magnet having a 2.5 millisecond pick-up time. With this rate of operation and the l6-card-point machine cycle above assumed, 625 record cards will be punched per minute. Assume now that when low points L of the cams 18 are at 0 relative to reference point Z, a pulse signal is delivered by one of the brushes 44 of station 45 to initiate energization of a particular magnet 62. When points L have rotated from point Z to the position shown in FIG. 2, high point H will register with follower 58 of element 16 and the 2.5 millisecond delay period will expire for causing the armature 59 to be attracted by magnet 62. The shoulder 61 of each element 16 and shoulder engaging surface 61a of each armature 59 are preferably beveled slightly and the corresponding follower 58 is normally spaced with very slight clearance away from the high points H, H of the corresponding cam 18. This will prevent the followers 58 from even grazing the high points of the cams during idling cycles yet permit the armatures to be freely attracted without substantial frictional resistance as the beveled surfaces 61a move slightly away from the corresponding beveled shoulders 61 and enable the followers 58 to he rocked very slightly by springs 57 into contact with either high point of their cams 18. However, if it is preferred that the magnet 62 be of the no-load type, the high points H, H may graze the followers 58 to rock the elements 16 very slightly with a wink motion against resistance of light springs 57 and thus completely unload the armatures 59 to permit them to be attracted without any opposition from springs 57. As used in claims, the recitation that the element 16 is normally held effectively disengaged from the cam is intended to cover either of these alternatives, for it will be noted that even if the no load magnet is preferred, the follower 58 will be fully disengaged from its cam 18 except when the high point H or H registers with said follower.

The element 16 will thus be freed from restraint by the holding means 19 when the armature 59 is attracted by magnet 62 at the instant low point L is 90 from point Z and high point H registers with follower 58. Magnet 62 will remain energized and hold armature 59 attracted until as shown in FIG. 6. Meanwhile, as soon as 7' element 16 is freed, spring 57 will rock it clockwise and maintain follower 58 in contact with cam 18 as point L moves from 90 to "180 from point Z and into registry with follower 58.

Meanwhile, when point L is 140 from point Z, the follower 58 will have been moved upward up sufiiciently relative to the end of interposer 15 to permit spring 52 to start to rock lever 14 clockwise about pin 50. Lever 14 will continue to move clockwise as point L moves from 140 to 235 from point Z (see FIG. 6), and shift interposer 15 rightward across the head of the punch 13 in a defined path assured by guide pin 55 and the movement of follower 53 in contact with cam 18. During this period and when point L is 170 from point Z, the various parts will be in the respective positions in which they are shown in FIG. 3.

During the period point L rotates from 180 to 270 from point Z, follower 58 will be moved downward by portion LH of cam 18 and element 16 will be rocked counterclockwise about pin 56. At 180 the downwardly moving follower 58 will contact the end of interposer 15 which will be moving rightward until 235 and then start moving leftward as follower 53 rides onto the part of cam 18 between points L and H and causes the cam to rock lever 14 counterclockwise. However, as point L rotates between 180 and 270 from point Z and high point H approaches follower 58, the cam 18 will act through the follower 58 and interposer 15 to move the punch 13 downward to a punching or marking position. During this period and with point L at 250 from point Z, the various parts will be in the positions in which they are shown in FIG. 4. As punch 13 moves down through a guide and stripper member 90, the toe and then the heel of the punch will pierce the card 12 and pass into a stationary die 91.

Meanwhile, as the punch 13 moves down, it will, through the hook 63, rock restoring lever 17 counterclockwise about pin 56 and thus swing follower 66 toward cam 18 against the light resistance of spring 64. After point L is 270 from point Z and positive down ward movement of the punch 13 ceases, cam point H will be rotated into registry with follower 66 and thus cause the cam 18 to rock lever 17 clockwise about pin 56 for positively, through book 63, moving punch 13 upward to its normal retracted position in which it contacts stop plate 65. After cam point H passes by follower 66, light spring 64 will maintain the punch 13 retracted and hold follower 66 effectively disengaged from the cam 18. The punch 13 will be restored to normal position when point L is 360 from point Z.

Assume now that no pulse has been given to the particular magnet 62 since the pulse which initiated the punching cycle just described. Under this condition, the magnet 62 will have remained deenergized after 120 and permitted armature 59 to be rockably biased by spring 60 toward element 16. As the element 16 is rocked counterclockwise by portion LH of cam 18 during the period point L rotates from 180 to 270, the shoulder-providing end of said element will move up along the side of armature 59 slightly past the point shown in FIG. 4 and corresponding to its position at 250; and at about 270, the spring 60 will pop the armature shoulder 61a in under shoulder 61.

If the bevels are provided on these shoulders, the armature spring 60 will impart a force sufficient to retract follower 58 enough to prevent it from being grazed by the high points H, H. After cam point H passes by follower 58 and point L rotates from 270 to 360 from point Z, the armature 59 will hold element 16 stationary and prevent it from being rocked by the cam and initiating another punching cycle. After point L is 320 from point Z and point H thus passes by follower 53, the cam 18 will cease rocking lever 14 counterclockwise and thus terminate leftward movement of interposer 15; and then as portion H-L' of the cam moves by'follower 5,3,,

spring 52 will try to rockt-he lever 14 clockwise but will be prevented from doing so because follower 58 will transmit via the interposer 15 a holding force sufficient to maintain follower 53 effectively disengaged from the cam, as above described. Thus, until the particular magnet 62 is again pulsed, the parts 14, 15, 16, 17, 13 will remain stationary (if no wink motion is provided) or essentially stationary (if wink motion is provided) in the relative positions shown in FIG. 2.

Assume now, however, that the particular brush 44 at station 4-5 also detects a perforation in the next row of the same column of the preceding card at said station and thus emits a pulse signal when point L is at for initiating a repeat punching cycle of the same punch 13. The various sequential operations during this repeat cycle will occur exactly 180 later than the punching cycle just completely described and they are denoted by dash lines in FIG. 6. Under the repeat punch condition now assumed, the only significant change in the sequence of operations described in connection with the first punch cycle is that the armature 59 will have remained attracted or will have been reattracted by the time point L is rotated 270 from point Z. This will prevent element 16 from being relatched by the armature 59 and thus cause a repetition of all of the sequential operations described in connection with the first punching cycle.

Referring now to FIG. 6, it will be noted that each of the sequential operations of the magnet 62, element 16, interposer 15, punch 13 and restoring lever 17 during a punching cycle is initiated before the preceding operation ends, thereby desirably reducing the overall time neces sary to complete a punch cycle and hence a full machine 0 cle.

It will now be apparent that each lever 14, interposer 15, element 16, restoring lever 17 and punch 13 is con trolled by a single rotating cam 18 in response to a pulse signal given at the proper time in a card point cycle to a corresponding magnet 62. Each rotating cam 18 preferably comprises two lobes of identical and symmetrical configuration to enable two punching operations to be performed during each revolution of the cam. The cams 18 are relatively flat adjacent their respective points L, H, L, H, to enable an overlapping of the sequential operations as shown in FIG. 6, also provide a smooth continuous motion whereby rate of change in acceleration of the parts 13, 14, 15, 16, 17 is reduced because changes in their direction of movement are effected gradually as these points rotate past the followers 53, 58, 66. After passing the relative flat portions adjacent the point L, H, L' or H as the case may be, these respective parts are accelerated rapidly and then decelerated rapidly as the followers 53, 58, 66 approach the fiat portion adjacent the succeeding one of said points.-

It will be apparent that the improved control mechanism may, if preferred, comprise a transversely elongated cam roll of the same configuration as cam 18 to control all of the marking or punch members 13, instead of providing a single cam 18 for each marking member 13. It will also be apparent that, if preferred, the followers 58, 53 and 66 could readily be controlled by separate cams or any desired combination of cams, rather than all of these followers being controlled in the illustrated manner by a single cam 18. Moreover, the improved control mechanism herein disclosed may be used to punch or otherwise mark records in the form of continuous tapes, as well as record cards. I

While the invention has been particularly shown and described with reference to a preferred embodiment thereof, it will be understood by those skilled in the art that various changes in form and details may be made therein without departing from the spirit and scope of the inven tion.

What is claimed is:

1. In a machine for marking a record, the combination of a member movable to a marking position to mark 9 the record, rotating cam means, actuating means comprising two parts positionable between the cam means and member to transmit motion from the cam means to the member to move the latter to marking position, means normally holding the actuating means effectively disengaged from the cam means, means operative to release the actuating means from the holding action of the holding means, and means operative upon operation of the releasing means to cause said actuating means to effectively engage said cam means and then be actuated thereby to selectively position said parts to cause said cam means to move the member to marking position.

2. In a machine for marking a record, the combination of a member movable to a marking position for marking the record, rotating cam means, two elements engageable with said cam means, means normally holding said elements effectively disengaged from said cam means, an interposer operably connected to one of said elements, and means for releasing said elements from restraint by said holding means to cause said one element to contact said cam means and through such contact move the interposer between the cam means and member to a position in which motion is transmitted from the cam means to the member via the other element and interposer for moving the member to marking position.

3. The combination according to claim 2, including restoring means operatively connected to said member and having a follower portion normally disengaged from said cam means, said follower portion being moved toward said cam means by and during movement of said member to marking position for causing said cam means after the member is marked to act through the follower portion of said restoring means to restore the member to a normal position in which it is spaced from the record.

4. The combination according to claim 2, wherein said cam means comprises a single rotating cam having a symmetrical cam surface, and wherein said elements are spaced about said cam to engage different parts of said surface when both of said elements are concurrenlty engaged.

5. In a machine for marking a record, the combination of a member movable to a marking position to mark the record, rotating cam means, an interposer positionable between the member and cam means, means providing two follower portions for engaging said cam means, one of said follower portions being disposed between the cam means and member, the other follower portion being operatively connected to said interposer, means normally holding said follower portions effectively disengaged from said cam means, means for freeing said follower portions from control by said holding means, separate means each effective upon freeing of said follower portions to actuate a respective one of said follower portions into contact with said cam means, said cam means being effective through contact with said follower portions to transmit motion via one of said follower portions and the interposer to the member for moving it to marking position.

6. In a machine for marking a record, the combination of a member movable to a marking position for marking the record, rotating cam means, an interposer interposable between the cam means and member, one element operably connected to said interposer, another element, means normally holding the other element in one position in which it is effectively disengaged from said cam means and exerts a force on said interposer to maintain said one element effectively disengaged from said cam means, means for releasing said other element from the action of said holding means, means operative upon operation of said releasing means to cause said other element to move into contact with said cam means and release said force on said interposer, and means responsive to release of said force to effect contact of said one element with said cam means to cause the latter through said one element to interpose said interposer between said member and other element, said cam means being effective follow- 10 ing interposition of said interposer to transmit motion via said interposer to said member for moving it to marking position. i

7. The combination according to claim 6, including restoring means operatively connected to said member and having a follower portion normally disengaged from said cam means, said follower portion being moved toward said cam means by and during movement of said member to marking position for causing said cam means after the member is marked to act through the follower portion of said restoring means to restore the member to a normal position in which it is spaced from the record.

8. The combination according to claim 6, including a rockable lever having one arm operatively connected to the member and another arm engageable with said cam means, said lever being rocked one Way by and during movement of said cam means to marking position to move said other arm toward said cam means, said cam means being thereafter operative through engagement with said other arm to rock said lever the opposite way to positively move said member out of marking position.

9. The combination according to claim 7, wherein said cam means comprises a single rotating cam having a cam surface defined by a plurality of lobes each of identical and symmetrical configuration and wherein said one element, other element and follower portion are arranged about said cam so as to engage different points of said surface when said elements and portion concurrently engage said cam.

10. In a machine for marking a record, the combination of a reciprocatable member movable from a normal position to a marking position for marking the record, a rotating cam, a rockable lever spring biased toward contact with said cam, an interposer pivotally connected to said lever and biased to extend in one direction into a space between said cam and member, a rockable element having an arm extending from the opposite direction into said space, holding means normally holding said element in a position in which said arm is effectively disengaged from said cam and abuts said interposer for operatively holding said lever disengaged from said cam, means responsive to release of said holding means torock said element out of abutting contact with said interposer and into engagement with said cam and cause the lever to be moved by its spring bias into contact said cam, whereupon as the cam rotates said lever will rock and interpose the interposer between said member and arm for causing said cam through said arm and interposer to move the member from normal position to marking position.

11. The combination according to claim 10, including a rockable restoring lever having one arm operatively connected to said member and another arm engageable with said cam, said restoring lever being rocked one way by and during movement of the member to marking position for rocking said other arm toward said cam, and said cam being effective after the record is marked to act through said other arm for rocking said restoring lever the opposite way to positively restore said member to normal position.

12. The combination according to claim 11, wherein said cam comprises a plurality of lobes of identical and symmetrical configuration for providing smooth harmonic motion of said levers and element while they are engaged with said cam.

13. The combination according to claim 11, including means for moving the record stepwise relative to the member, and means interconnecting the cam and last named means for coordinating their movements so that the record will be advanced stepwise a certain whole number of times for each complete revolution of said cam, and wherein said cam comprises a corresponding certain number of lobes of identical and symmetrical configuration, whereby the record may be marked said certain number of times for each revolution of the cam.

14. In a machine for marking a record, the combination of a member movable to a marking position for marking the record, rotating cam means, an interposer interposable between the cam means and member, one element operably connected to said interposer, another element, means normally holding the other element in one position in which it exerts a force on said interposer to maintain said one element and interposer eifectively disengaged from said cam means, means for releasing said other element from the action of said holding means, means operative 10 upon operation of said releasing means to cause said other element to release said force on said interposer,

12 and means responsive to release of said force to efiect contact of said one element with said cam means to cause the latter through said one element to interpose said interposer between said member and cam means to cause motion to be transmitted from the cam means via said interposer to said member to move the latter to marking position.

References Cited in the file of this patent UNITED STATES PATENTS 

